Heat exchanger having a vortex tube for controlled airflow applications

ABSTRACT

A heat exchanger device is provided. The device includes, but is not limited to, a vortex tube and a hollow tube. The vortex tube includes, but is not limited to, a fluid supply tube connected with a swirl chamber, an inlet of a first inner tube connected with an outlet of the swirl chamber and an inlet of a second inner tube connected with the outlet of the swirl chamber, an internal heat exchanger, wherein an inlet of the internal heat exchanger is connected with an outlet of the first inner tube, and a nozzle connected with the outlet of the first inner tube and the inlet of the internal heat exchanger. The hollow tube is connected with an inlet of the nozzle.

CROSS-REFERENCES TO RELATED APPLICATIONS

The Present Application claims priority to U.S. Provisional PatentApplication No. 61/263,817, filed 23 Nov. 2009. The content of this U.S.Provisional Patent Application is hereby incorporated herein in itsentirety.

FIELD OF THE INVENTION

The present invention relates generally to controlled airflow devicesand, more particularly, to a heat exchanger device having a vortex tubefor controlled airflow applications.

BACKGROUND OF THE INVENTION

Certain applications require a small amount of cold or hot air that mustbe delivered through small diameter restrictive tubing or hose, (e.g.tubing with an inner diameter of less than 10 millimeters, andpreferably, less than 3 millimeters), sometimes because of theconstricted space that the tubing must be routed through. Theseapplications are widespread and can vary from aerospace to electronicsto medical uses as well as others. These applications normally may onlyrequire a small amount of cooling or heating capacity, normally nogreater than 150 BTUH (44 watts).

One conventional method to deliver cold airflows is refrigeration-basedair conditioning systems. Typically, these refrigeration-based units aredesigned to deliver relatively large airflows through large ducts orpassages. Because of this, they are designed so that the cold airflowcan be moved with a fan or blower; the fan or blower can overcome thelow ducting resistances of the relatively large passages. Application ofthese conventional refrigeration systems for providing cold airflowsthrough small sized passages or tubing is not ideal because the fans andblowers used to convey the cold air cannot overcome the resistance ofthe small passages. In some instances, the refrigeration system can bedesigned or retrofitted with higher pressure blowers or fans to overcomethe ducting resistance, but these blowers are intended for deliveringlarge volume airflows, not airflows on the order of less than 2 or 3cubic feet per minute (0.000944 m³/s or 0.00142 m³/s). In addition,these conventional refrigeration systems typically range from 350 to12,000 BTUH (102.57 Watts to 3,516.85 Watts) cooling capacity, even thesmallest known units are considered oversized for most applications.

As a result it would be desirable to have a heat exchanger which candeliver cold or hot air through very small diameter restrictive tubingor hose to a site for cooling or heating that location.

SUMMARY

The present invention is defined by the following claims, and nothing inthis section should be taken as a limitation on those claims.

In one aspect, a heat exchanger device is provided. The device includes,but is not limited to, a vortex tube and a hollow tube. The vortex tubeincludes, but is not limited to, a fluid supply tube connected with aswirl chamber, an inlet of a first inner tube connected with an outletof the swirl chamber and an inlet of a second inner tube connected withthe outlet of the swirl chamber, an internal heat exchanger, wherein aninlet of the internal heat exchanger is connected with an outlet of thefirst inner tube, and a nozzle connected with the outlet of the firstinner tube and the inlet of the internal heat exchanger. The hollow tubeis connected with an inlet of the nozzle.

In one aspect, a method for heating or cooling is provided. The methodincludes, but is not limited to, supplying fluid into a vortex tube, thevortex tube having a first inner tube connected with a swirl chamber andan outer backpressure tube surrounding the first inner tube. The methodfurther includes, but is not limited to, dividing the fluid into firstand second streams of fluid, flowing the first stream of fluid throughthe first inner tube, and flowing a first portion of the first stream offluid through a nozzle connected with the first inner tube. The methodfurther includes, but is not limited to, flowing a second portion of thefirst stream of fluid through the outer backpressure tube.

In one aspect, a device for heating or cooling a site is provided. Thedevice includes, but is not limited to, a swirl chamber for receivingand separating a fluid into first and second streams, a first inner tubeconnected with an outlet of the swirl chamber, a backpressure tube, anda nozzle. The backpressure tube has an inlet. The inlet of the outerbackpressure tube is connected with an outlet of the first inner tube.The nozzle is connected with the outlet of the first inner tube and theinlet of the backpressure tube.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention can be better understood with reference to the followingdrawings and description. The components in the figures are notnecessarily to scale, emphasis instead being placed upon illustratingthe principles of the invention.

FIG. 1A depicts a side view of a heat exchanger including a vortex tubeconnected with a small diameter tube having an adjustment valve at thevortex tube, in accordance with one preferred embodiment.

FIG. 1B depicts an end view taken along line A-A of the vortex tube forthe heat exchanger shown in FIG. 1A, in accordance with one preferredembodiment.

FIG. 2A depicts an insulating sleeve assembly of the vortex tube for theheat exchanger shown in FIG. 1A, in accordance with one preferredembodiment. The insulating sleeve assembly is made of a thermallyinsulating material (plastic, ceramic, etc.) whose purpose is toinsulate an external sleeve 112 from cold or hot exhaust flow 154.

FIG. 2B depicts an exploded top view of the insulating sleeve assemblyof the vortex tube for the heat exchanger shown in FIG. 2A, inaccordance with one preferred embodiment. Insulating sleeves 113 and 115fit together to form a continuous insulating sleeve inside externalsleeve 112.

FIG. 2C depicts a partial cross-sectional side view taken along line G-Gof the heat exchanger shown in FIG. 1B, in accordance with one preferredembodiment.

FIG. 2D depicts a first end view taken along line B-B of the vortex tubefor the heat exchanger shown in FIG. 1A, in accordance with onepreferred embodiment.

FIG. 2E depicts a cross-sectional view taken along line J-J of thevortex tube for the heat exchanger shown in FIG. 2C, in accordance withone preferred embodiment.

FIG. 2F depicts a cross-sectional view taken along line C-C of thevortex tube for the heat exchanger shown in FIG. 2C, in accordance withone preferred embodiment.

FIG. 2G depicts a cross-sectional view taken along line D-D of thevortex tube for the heat exchanger shown in FIG. 2C, in accordance withone preferred embodiment.

FIG. 2H depicts a cross-sectional view taken along line K-K of thevortex tube for the heat exchanger shown in FIG. 2C, in accordance withone preferred embodiment.

FIG. 2I depicts a cross-sectional view taken along line F-F of thevortex tube for the heat exchanger shown in FIG. 2C, in accordance withone preferred embodiment.

FIG. 2J depicts a second end view taken along line L-L of the vortextube for the heat exchanger shown in FIG. 2C, in accordance with onepreferred embodiment.

FIG. 3 depicts an enlarged partial cross-sectional side view taken alongline G-G of the heat exchanger shown in FIG. 1B, in accordance with onepreferred embodiment.

DETAILED DESCRIPTION

Methods and devices consistent with the present invention overcome thedisadvantages of conventional cooling and heating systems by using avortex tube which has a means for reducing backpressure produced whenfluid flows through small diameter restrictive tubing, maximizing theefficiency of the vortex tube heat exchanger.

Referring to FIGS. 1-3, there is shown various embodiments of a heatexchanger device 100 for cooling applications consistent with thepresent invention. Alternately a vortex tube 110 of the heat exchangerdevice 100 may be reversed for heating applications.

Referring to FIGS. 1A and 1B, heat exchanger device 100 includes avortex tube 110 connected via with a small diameter restrictive tube 180via a first inner tube 142. Small diameter restrictive tube 180 is ahollow tube having a diameter D₂ preferably of less than 10 millimeters,and more preferably, less than 5 millimeters, and most preferably lessthan 3 millimeters. In one embodiment, the small diameter restrictivetube 180 has a diameter D₂ of approximately 2.413 millimeters±0.5millimeters. In one embodiment, small diameter restrictive tube 180 is acannula which is used for insertion into a mammalian subject. Methodsand systems consistent with the present invention take all of the aboveconcerns into account in order to maximize the efficiency of the vortextube 110.

Referring to FIGS. 2A, 2B, 2C, 2D, 2E, 2F, 2G, 2H, 2I, 2J, and 3, vortextube 110 includes fluid supply tube 120 connected with inlet 123 ofvortex tube 110, a swirl chamber 140 connected with the fluid supplytube 120, a first inner tube 142 and second inner tube 160, preferablyfor hot fluids, connected with the swirl chamber 140, a backpressuretube 150 connected with the first inner tube 142, and a nozzle 144connected with an outlet 124 of the first inner tube 142.

Vortex tube 110 receives a fluid 104 through the fluid supply tube 120,and separates fluid 104 into first and second streams 106, 108 of fluid104 traveling down first and second inner tubes 142, 160, respectively.Preferably, the fluid 104 is received at an ambient temperature from 15°C. to 30° C., and more preferably about 21.1° C.±5° C. In oneembodiment, the first stream 106 is a cold stream of fluid 104 and thesecond stream 108 is a hot stream of fluid 104. In one embodiment, thesecond stream 108 is a cold stream of fluid 104 and the first stream 106is a hot stream of fluid 104. Preferably, a cold stream of fluid 104 hasan average temperature of less than 5° C., more preferably less than 0°C., more preferably less than −5° C., and most preferably less than −10°C. Preferably, a hot stream of fluid 104 has an average temperature ofmore than 60° C., more preferably more than 65° C., more preferably morethan 70° C., and most preferably more than 80° C. Fluid 104 is anymaterial in gaseous form. Preferably, fluid 104 is a compressed gas,such as compressed air.

Vortex tube 110 may be used for controlled airflow applications. In oneembodiment, vortex tube 110 can deliver cold airflows from zero to 100cubic feet/minute (CFM) (zero to 2.832 cubic meters/minute), using onlycompressed air as a power source. In one embodiment, a smaller vortextube 110 can create cooling capacities up to 400 BTUH (117 Watts) usingno more than 8 standard cubic feet/minute (SCFM) (0.22656 cubicmeters/minute) of compressed air. Vortex tube 110 performs mostefficiently when first fluid stream 106 is exhausted from the vortextube 110 and into small diameter restrictive tube 180 at atmosphericpressure with no resistance to flow. Vortex tube 110 can still performwell with slight resistance or backpressure on the first fluid stream106. However, in certain controlled airflow applications, theresistances created by the small diameter restrictive tube 180 intowhich the first fluid stream 106 flows, can create a backpressure whichexceeds 19.7 psia (34.5 kPa) at an outlet 124 of the first inner tube142 of the vortex tube 110, where the first fluid stream 106 flows intothe tube 180. Because the performance of vortex tube 110 is directlyrelated to the absolute pressure differential between the pressure ofthe fluid 104 at an inlet 123 and the pressure of the fluid 104 in firststream 106 at the outlet 124, a 19.7 psia (34.5 kPa) resistance orbackpressure can severely limit the performance of the vortex tube 110.

For example, in a typical vortex tube application the pressure of thefluid 104 at the inlet 123 of the vortex tube 110 could be as little as54.7 psia (377.1 kPa) and the pressure of the fluid 104, andparticularly first stream 106 of fluid 104, at the outlet 124 could bethat of air directed to atmosphere, or 14.7 psia (101.325 kPa). In thisexample, the pressure drop ratio is 54.7/14.7=3.72:1. Ideally, thedesired pressure at the inlet 123 is 104.7 to 114.7 psia (721.9 kPa to790.8 kPa) and desired pressure at the outlet 124 is 14.7 psia (101.325kPa). Therefore the ideal pressure drop ratio is 114.7/14.7=7.8:1, orgreater. In a controlled airflow application where the first stream 106of fluid 104 is subject to 19.7 psia (34.5 kPa) of backpressure, thepressure drop ratio becomes as little as 54.7/19.7=2.77:1. Since thepressure drop ratio determines the performance of the vortex tube 110,higher pressure drop ratios mean better performance and betterefficiency of the vortex tube 110. As a result, one object of thisinvention is to keep the pressure drop ratio as high as possible, andpreferably greater than 4.00:1, and more preferably, greater than5.00:1, and most preferably, greater than 7.00:1.

Vortex tube 110 is most efficient when operated in a 60 to 70% cold/heatfraction range. This means that an 8 SCFM (0.22656 cubic meters/minute)vortex tube 110 is most efficient in creating the most cooling capacity(BTUH) when there is 60 to 70% of this 8 SCFM (0.22656 cubicmeters/minute) of fluid 104 exiting out the outlet 124 of first innertube 142. Even when operated in this cold/heat fraction range and atreasonable pressure drop ratios (e.g. pressure drop ratios of greaterthan greater than 4.00:1), very cold or very hot air temperatures (e.g.less than −5° C. or greater than 65° C., respectively) are achievable.

In certain controlled airflow applications, length L₃ of small diameterrestrictive tube 180 connected with outlet 124 of the vortex tube 110can be quite long in length (for example, greater than 1 meter, and morepreferably greater than two meters, and in one example up to up to 3.04meters), for various reasons. The application may require that cold orhot fluid 104 be present at an outlet 184 of the small diameterrestrictive tube 180 in a short time period (e.g. no longer than 5minutes). The length L₃, diameter D₂, wall thickness, and material ofsmall diameter restrictive tube 180 determines its thermal mass. Becausethe cooling capacity of the driving vortex tube 110 can be limited (e.g.to 150 BTUH (43.875 Watts) or less), the thermal mass of the smalldiameter restrictive tube 180 must be kept to a minimum, to allow quickrealization of the cold or hot temperature of the fluid 104 at theoutlet 184 of the small diameter restrictive tube 180. Alternately, orin addition to this, the small diameter restrictive tube 180 can bepre-cooled or cooled concurrently via a heat exchanger to allowun-delayed cold (or hot) temperatures of fluid 104 at the outlet 184 inorder to minimize any “thermal lag”.

Fluid supply tube 120 is connected with inlet 123 of vortex tube 110 andsupplies fluid 104 to vortex tube 110 at inlet 123. Preferably, supplytube 120 is movably connected with inlet 123 using a swivelingelbow-shaped member 122, allowing for the fluid supply tube 120 to berotated about inlet 123. Inlet 123 is connected with an entry channel118 which leads into the vortex tube 110, and specifically into theswirl chamber 140. Alternatively, fluid supply tube 120 may be routedinside the external sleeve 112 and then out the back of the vortex tube110 through exhaust cover 171.

Fluid 104 enters swirl chamber 140, and is separated by swirl chamber140 into first and second streams 106, 108 of fluid 104 traveling downfirst and second inner tubes 142, 160, respectively. In one embodiment,the first stream 106 is a cold stream of fluid 104 and the second stream108 is a hot stream of fluid 104. In one embodiment, the second stream108 is a cold stream of fluid 104 and the first stream 106 is a hotstream of fluid 104.

An inlet 141 of the first inner tube 142 is connected with a firstoutlet 139 of the swirl chamber 140, and an inlet 161 of the secondinner tube 160 is connected with a second outlet 143 of the swirlchamber 140. In this manner, as swirl chamber 140 separates fluid 104 into first and second streams 106, 108, each stream 106, 108 is thenguided down its respective inner tube 142, 160.

First inner tube 142 allows for the first stream 106 of fluid 104 toflow from the swirl chamber to nozzle 144. Outlet 124 of first innertube 142 is connected with nozzle 144 and backpressure tube 150. Nozzle144 is sized so as not to allow all of the first stream 106 of fluid 104to flow through nozzle 144 without an increase in pressure, or withoutforming any backpressure in first stream 106. In one embodiment, aninlet of the nozzle 144 is smaller than outlet 124 of the first innertube 142 and is capable of creating backpressure in the first stream106.

As a result, in order to prevent any backpressure from forming in thefirst stream 106 in first inner tube 142, the vortex tube 110 includesbackpressure tube 150 which is designed to take in any excess fluid 104which cannot freely flow through nozzle 144. As the first stream 106 offluid 104 flows through the first inner tube 142, a first portion 152 ofthe first stream 106 is able to freely exit through the nozzle 144 and asecond portion 154 of the first stream 106 of fluid 104 entersbackpressure tube 150. By allowing for another passageway for excessfluid 104 to go to, the backpressure tube 150 is able to relievebackpressure in first stream 106 that may be caused as fluid 104 flowsthrough nozzle 144, helping maximize the efficiency of the vortex tube110.

In one embodiment, the backpressure tube 150 in addition to relievingany backpressure in first stream 106, can be configured as an internalheat exchanger 148 to transfer cold/heat to the first inner tube 142and/or the second inner tube 160. When configured as an internal heatexchanger 148, backpressure tube 150 can take several forms, such as anouter backpressure tube which surrounds the inner tubes 142, 160, acoiled tube surrounding inner tubes 142, 160, a plate type deviceconnected with inner tubes 142, 160, a shell and tube type, and a finnedtube connected with inner tubes 142, 160. A shell and tube type heatexchanger includes several small tubes enclosed in a larger shell. Inone embodiment, the backpressure tube 150 is an outer backpressure tubewhich preferably surrounds at least a portion of the first inner tube142.

Preferably, the backpressure tube 150 comprises a material which has athermal conductivity of less than 10 Watts per meter Kelvin and theinner tubes 142, 160 have a thermal conductivity of greater than 10Watts per meter Kelvin. As a result, a good portion of the heat or coldfrom the second portion 154 of the first stream 106 which enters thebackpressure tube 150 can be transferred to the inner tubes 142, 160,helping maximize the efficiency of the vortex tube 110.

In one embodiment, the backpressure tube 150 is an outer backpressuretube which comprises a material which has a thermal conductivity of lessthan 10 Watts per meter Kelvin and the inner tubes 142, 160 have athermal conductivity of greater than 10 Watts per meter Kelvin. As aresult, heat or cold from the second portion 154 of the first stream 106which enters the outer backpressure tube is transferred to the innertubes 142, 160.

Second inner tube 160 allows for the second stream 108 of fluid 104 toflow from the swirl chamber 140 to an exhaust chamber 170. At theexhaust chamber 170, the second stream 108 of fluid 104 mixes with asecond portion 154 of the first stream 106 of fluid 104. Upon mixing,the combined streams of fluid 104 are then exhausted from the vortextube 110 through exhaust holes 172 formed in an exhaust cover 171 whichcaps the exhaust chamber 170. The temperature of the combined streams offluid 104 which are exhausted from the vortex tube 110 can be controlledby controlling the amount of the second portion 154 which enters theexhaust chamber 170, using means such as a flow control mechanism 130.Second inner tube 160 allows for the second stream 108 of fluid 104 toflow from the swirl chamber 140 out through the vortex tube 110 via avalve or orifice 165. The adjustable valve or fixed orifice 165 allowsthe vortex tube 110 to be adjusted, in the field with the case of theadjustable valve or at the factory in the case of the fixed orifice, tomaintain an optimum cold fraction of 60% to 70%. As the second stream108 of fluid 104 passes out the valve or orifice 165, it enters anexhaust chamber 170.

Flow control mechanism 130 is any device which can vary the flow offluid 104 through a tube or channel, and includes things such as avalve. In one embodiment, the flow control mechanism 130 includes aninner flow control ring 132 having openings 133 through which secondportion 154 of first stream 106 flows through, and an outer flow controlring 134 having openings 135 through which second portion 154 of firststream 106 flows through. Preferably, one of the rings 132, 134 is fixedwhile the other ring 132, 134 is movable, in order to create aconfiguration in which the size of the openings 133 can be varied andtherefore the flow of the second portion 154 of first stream 106 can bevaried as well. The flow control mechanism 130 is for regulating anamount of fluid 104 allowed to flow through the backpressure tube 150,and in turn regulating an amount of fluid 104 able to flow through thenozzle 144 and into the small diameter restrictive tube 180. Acompression spring 137 can be placed between body 191 of the vortex tube110 and the outer flow control ring 134. This compression spring 137serves to prevent gaps and air leakage between outer flow control ring134 and inner flow control ring 132.

In operation, fluid 104, such as compressed air, enters the vortex tube110 through fluid supply tube 120 at inlet 123. The vortex tube 110 isset at a fixed cold/heat fraction of preferably from 50% to 90%, andmore preferably from 60% to 80%, and most preferably, from 60% to 70%.As used herein, the term cold/heat fraction refers to the percentage ofthe total flow of fluid 104 through the vortex tube 110 which existsfrom inner tube 142 as a cold/hot stream of fluid 104.

The vortex tube 110 divides the fluid 104 into first and second streams106, 108 of fluid 104. The first stream 106 is a fraction of fluid 104equal to the fixed cold/heat fraction. First stream 106 flows down thefirst inner tube 142 and exits outlet 124 of first inner tube 142. Afirst portion 152 of the first stream 106 enters the nozzle 144, while asecond portion 154 of the first stream 106 enters and flows down thebackpressure tube 150. The first inner tube 142 is ideally sized to notcreate a flow restriction of the first stream 106, but not so large asto add unnecessary thermal mass to the backpressure tube 150. The firstinner tube 142 is preferably constructed of a material that has a highthermal conductivity, for example, a thermal conductivity greater than10 Watts per meter Kelvin. As the first stream 106 exits the outlet 124of the first inner tube 142 and into the nozzle 144, second portion 154of the first stream 106 flows back through the backpressure tube 150.

Backpressure tube 150 is sized so as not to create a flow restriction tothe second portion 154 but also not so large to prevent unnecessarythermal mass. Preferably, the backpressure tube 150 is constructed of amaterial that has a low thermal conductivity, for example, a thermalconductivity of less than 10 Watts per meter Kelvin. The second portion154 of the first stream 106 that passes back over the inner tube 142 andenters the backpressure tube 150 is also known as an exhaust flow. Thesecond portion 154 serves to keep the first stream 106 traveling throughthe first inner tube 142 either cool or warm, depending on theapplication and the configuration of the vortex tube 110. This secondportion 154 can either be adjusted by the user or fixed to create acertain heat exchange rate. If adjustable, the flow of the secondportion 154 can be adjusted via flow control mechanism 130, such as avalve, at either end of the backpressure tube 150.

The first portion 152 which is not directed back through thebackpressure tube 150 and which flows through the nozzle 144 may also bereferred to as the application flow. The first portion 152 is theportion of the first stream 106 that is directed to the point of use orapplication site 102. In one embodiment, adjustment of the flow of thesecond portion 154 through the backpressure tube 150 via flow controlmechanism 130, also adjusts the flow of the first portion 152 flowingthrough the nozzle 144 to the application site 102.

For example, suppose 8 CFM (0.227 cubic·meters/minute) of compressed airenters the vortex tube and 4.77 CFM (0.135 cubic·meters/minute) exitsthe outlet 124 as the cold/hot fraction of the total amount of fluid104. The 4.77 CFM (0.135 cubic·meters/minute) cold/hot fraction isrouted through the first inner tube 142 of the vortex tube 110. As the4.77 CFM (0.135 cubic·meters/minute) cold/hot fraction of the totalamount of fluid 104 exits the vortex tube 110, a second portion 154 ofthe 4.77 CFM cold/hot fraction (4.24 CFM, for example) is then directedback through the backpressure tube 150. This second portion 154 is thecold/hot exhaust flow and keeps the cold/hot fraction from gaining orlosing heat in the first inner tube 142. The remaining 0.53 CFM of fluid104 is directed to the application site 102 and is called theapplication flow. The percentage of cold/hot exhaust flow to applicationflow can either be a fixed percentage or can be adjustable by the user,via flow control mechanism 130. In the current example, the percentageof application flow to exhaust flow is 0.53/4.24=12.5%. The cold/hotexhaust fraction in second stream 108 from the vortex tube 110 in thisexample is 3.23 CFM.

The second portion 154 of the first stream 106 of fluid 104 is routed ina counterflow direction (opposite that of the direction of flow of thefirst stream 106) back through the backpressure tube 150 to either keepthe cold stream of fluid 104 in first inner tube 142 from gaining heator keep the hot stream of fluid 104 in first inner tube 142 from losingheat, and the remaining portion 152 of the first stream 106 of fluid 104is directed to the application site 102. The first portion 152, theapplication flow, is therefore kept as cold or hot as possible as itreaches the application site 102, prolonging its cooling or heatingcapacity.

As the flow of the second portion 154 is channeled through the valvecreated by passages 133 and 135 in inner flow control ring 132 and outerflow control ring 134, it exits passages 135 into an insulated exhaustchamber 190. Insulated exhaust chamber 190 is formed by two insulatedplastic sleeves 113 and 115. Sleeves 113 and 115 fit tightly around body191 of vortex tube 110 and insulate the exterior sleeve 112 from cold orhot flow in second portion 154. Insulating the exterior sleeve 112 isimportant as this allows vortex tube 110 to be a hand-held device andprovides comfort to a user of the vortex tube 110 when held by a hand.

With reference to FIG. 2F, as the flow of the second portion 154 entersinsulated chamber 190, it flows around the body 191 of the vortex tube110 through passages 195. As flow from the second portion 154 continuesthrough passages 195, it flows between hot tube 160 and insulated sleeve113. Flow from the second portion 154 continues on and flows through theholes 196 formed in the intermediate cap 197, as shown in FIG. 2J.Intermediate cap 197 serves to keep the cold/hot flow from the secondportion 154 separate from the hot/cold exhaust flow 198. As flow 154passes through holes 196 in intermediate cap 197, it enters exhaustchamber 170 and mixes with the hot/cold exhaust flow 108.

The hot/cold exhaust flow 108, as it exits vortex tube 110, passesthrough a muffler 199. Muffler 199 serves to keep exhaust flow 108 quietin order to reduce noise for a user handling the vortex tube 110.Muffler 199 can be made of any porous noise reducing material, andpreferably, a porous plastic material. Muffler 199 must be porous enoughso as not to create a backpressure on exhaust flow 108. Hot/cold exhaustflow 108, as it passes through muffler 199, then mixes with cold/hotexhaust flow 154 in chamber 200. Chamber 200 is formed between muffler199 and external sleeve 112. As exhaust flows 154 and 108 mix in chamber200, the hot and cold temperatures of exhaust flows 154 and 108 tend tocancel each other out, resulting in an exhaust temperature preferably ofabout 21° C.±5° C. The exhaust temperature is preferably notobjectionable to a user of the vortex tube 110. After exhaust flows 154and 108 mix in chamber 200, a combined exhaust flow 201 exists out ofvortex tube 110 from exhaust cover 171 via openings 172.

The Abstract of the Disclosure is provided to allow the reader toquickly ascertain the nature of the technical disclosure. It issubmitted with the understanding that it will not be used to interpretor limit the scope or meaning of the claims. In addition, in theforegoing Detailed Description, it can be seen that various features aregrouped together in various embodiments for the purpose of streamliningthe disclosure. This method of disclosure is not to be interpreted asreflecting an intention that the claimed embodiments require morefeatures than are expressly recited in each claim. Rather, as thefollowing claims reflect, inventive subject matter lies in less than allfeatures of a single disclosed embodiment. Thus the following claims arehereby incorporated into the Detailed Description, with each claimstanding on its own as a separately claimed subject matter.

While various embodiments of the invention have been described, it willbe apparent to those of ordinary skill in the art that other embodimentsand implementations are possible within the scope of the invention.Accordingly, the invention is not to be restricted except in light ofthe attached claims and their equivalents.

1. A heat exchanger device comprising: a vortex tube, wherein the vortextube includes: a fluid supply tube connected with a swirl chamber, aninlet of a first inner tube connected with an outlet of the swirlchamber and an inlet of a second inner tube connected with the outlet ofthe swirl chamber, an internal heat exchanger, wherein an inlet of theinternal heat exchanger is connected with an outlet of the first innertube, and a nozzle connected with the outlet of the first inner tube andthe inlet of the internal heat exchanger; and a hollow tube connectedwith an inlet of the nozzle.
 2. The device of claim 1, wherein theinternal heat exchanger is an outer backpressure tube which surroundsthe first inner tube and the second inner tube.
 3. The device of claim2, wherein the outer backpressure tube has a thermal conductivity ofless than 10 Watts per meter Kelvin and the first inner tube has athermal conductivity of greater than 10 Watts per meter Kelvin.
 4. Thedevice of claim 1, wherein the vortex tube is sized so as to allow acompressed fluid to travel into the swirling chamber and be divided intofirst and second streams of fluid, wherein the first stream of fluid isable to flow through the first inner tube, and wherein a first portionof the first stream of fluid is able to exit through the nozzle and asecond portion of the first stream of fluid is able to enter theinternal heat exchanger.
 5. The device of claim 4, wherein the firststream comprises a cooling fluid and the second stream comprises aheating fluid.
 6. The device of claim 1, wherein the vortex tube furthercomprises a flow control mechanism for regulating an amount of fluidallowed to flow through the internal heat exchanger, and in turnregulating an amount of fluid able to flow through the nozzle.
 7. Thedevice of claim 1, wherein the vortex tube further comprises an exhaustchamber connected with an outlet of the internal heat exchanger and anoutlet of the second inner tube.
 8. A method for heating or coolingcomprising: supplying fluid into a vortex tube, the vortex tube having afirst inner tube connected with a swirl chamber and an outerbackpressure tube surrounding the first inner tube; dividing the fluidinto first and second streams of fluid; flowing the first stream offluid through the first inner tube; flowing a first portion of the firststream of fluid through a nozzle connected with the first inner tube;and flowing a second portion of the first stream of fluid through theouter backpressure tube.
 9. The method of claim 8, wherein the supplyingof fluid further comprises supplying a compressed fluid into a swirlchamber of a vortex tube.
 10. The method of claim 8, wherein flowing ofthe first portion of the first stream is through the nozzle and into asmall diameter restrictive tube.
 11. The method of claim 8, furthercomprising: flowing the second stream of fluid through a second innertube; and combining the second stream of fluid with the second portionof the first stream of fluid in an exhaust chamber connected with anoutlet of the outer backpressure tube and an outlet of the second innertube.
 12. The method of claim 8, wherein the first stream comprises acooling fluid and the second stream comprises a heating fluid.
 13. Themethod of claim 12, wherein the fluid is compressed air.
 14. A devicefor heating or cooling a site comprising: a swirl chamber for receivingand separating a fluid into first and second streams; a first inner tubeconnected with an outlet of the swirl chamber; a backpressure tubehaving an inlet, wherein the inlet of the outer backpressure tube isconnected with an outlet of the first inner tube; and a nozzle connectedwith the outlet of the first inner tube and the inlet of thebackpressure tube.
 15. The device of claim 14, wherein an inlet of thenozzle is smaller than an outlet of the first inner tube and which iscapable of creating backpressure in the first stream, and wherein thebackpressure tube is capable of relieving backpressure created in thefirst stream.
 16. The device of claim 14, further comprising a smalldiameter restrictive tube connected with the nozzle capable of directinga portion of the first stream received from the first inner tube to thesite.
 17. The device of claim 14, wherein the backpressure tube has athermal conductivity of less than 10 Watts per meter Kelvin and thefirst inner tube has a thermal conductivity of greater than 10 Watts permeter Kelvin.
 18. The device of claim 14, further comprising an exhaustchamber connected with an outlet of the backpressure tube and an outletof the second inner tube.
 19. The device of claim 14, wherein the fluidcomprises compressed air.
 20. The device of claim 14 further comprisinga flow control mechanism for regulating an amount of fluid allowed toflow through the backpressure tube.